Brake and braking system



Feb. 16, 1960 N. E. KLEIN ETAL 2,924,869

BRAKE AND BRAKING SYSTEM Filed March 1, 1954 4 Sheets-Sheet l i: v I.

INVENTOR.

NORMAN E. KLEIN CHARLES D. LUCAS GEORGE A. MOBLEY ATTORNEY WM KM Feb.16, 1960 Filed March 1 1954 N. E. KLEIN ETAL BRAKE AND BRAKING SYSTEM 4Sheets-Sheet 2 FIG-2- PUMP IN V EN TOR.

NORMAN E. KLEIN CHARLES o. LUCAS GEORGE A MOBLEY BY WKZM M ATTORNEY N.E. KLEIN ET AL BRAKE AND BRAKING SYSTEM Feb. 16, 1960 v 4 Sheets-Sheet 3Filed March 1, 1954 INVENTOR. NORMAN E. KLEIN BY EORGE A. uloaLEvATTORNEY Feb. 16,1960

Filed March 1, 1954 N. E. KLE lN E L BRAKE AND BRAKING SYSTEM as 6 0 6263 5s 59 50 4 Sheets-Sheet 4 INVENTOR.

NORMAN E.KLEIN CHARL a. was esoas .MOBLEY wlzaiw ATTORNEY fl dstatesPatent 2,924,869. BRAKE AND BRAKING SYS'IEM search Corporation. nearPeudleton', S.C .,a corporation qf e a ar ApplicatiouMareh 1, 1954,Serial No. 413,132

I to. 2

This: invention relates to brakes and braking systems and: moreparticularly to fluid braking systems suitable for usewith textilebeaming or slashing apparatus and a new type of fluid activated brakesuitable for use in such}. a braking system. In beaming and slashing.operations it is common practice toload a creel with a number of-sectionbeams each of which has been previously wound with a multitude of warpthreadsor ends. The endsfrom all of the section. beams are combined toform a warp. which is, at least in slashing operations, then treatedwith a liquid size dried and wound on a warp beam. In all such beamingoperations it is necessary that the section beams be braked in order toprovide the. proper tension in the warp and to,prevent t he warp fromoverrunning during such times as the apparatus is being brought to astop. At present, braking action for the. section beams is customarilyprovided by placing a weighted rope'or band around one or both heads ofeach of the section beams in peripheral grooves provided for thepurpose. In spite of mnnerous suggestions over a period of many yearsfor replacing such brakes with a more precise system, rope bralgescontinue as the choieeof most of the industry.

The disadvantages of weighted rope brakes are'well recognized in theart. The brakes require constant attention since asthe diameter of theyarn supply on each of the section beams decreases, it is necessary todecrease the braking action to ,maintan a constant tension in the warpand this. means that an operator must be continually removing weightsfrom the rope brakes on each of the section beams throughout the beamingoperation, A second well recognized disadvantage of rope brak isthat thebraking action is not decreased uni- ,fo as thefweights are removed, andone obtains a step wise reduction of braking action. A further seriousdisadvantage of the weighted rope brakes is that the ropes soon becomefrayed so that the braking action on various section beams is notuniform and, as a result, some section beams run out of yarn much soonean oth r -j A e rn remaining a t n be is, out cannot readily be employedin the preparaum Qff arp. s, e ults n ha s. n n h r d s t w te, a

In spite of the fact that the disadvantages of rope brakes for beamingapparatus have'been recognized for 'rnany years and many efforts havebeen made to replace the r pe brakes, none of these efforts have metwith any degree ofcommercial success. A primary reason that theseefforts have not been successful is that conventio al mechanical brakesin all instances possess measu able operating friction in the controlsystem i which results: in objectional hysteresischaracteristics. Inother words. the amount of braking torque obtained with the applicatiouof a given force to the'brake activating varies vWith conventional mychanical brakes derenfiii e rm Whether. th se ted. al i app from asmaller value or from alarger value. "'-'Afurther ice reason why theseefforts have been largely unsuccessful is that conventional brakesordinarily do not have a linear response so, that the amount of brakingtorque resultingfrom the application of'the brake is not necessarilyproportional to the amount of force applied to the brake activatingmeans. A still further reason why these efforts have generally met withfailure is that there has not been available a braking system capable ofevenly compensating for the different brakingtorques required as thediameter of the section beams is decreased.

According to this invention thereis provided a brake suitable foruse onsection beams wherein two disk shaped braking surfaces are engaged infrictional contact by theexpansion of a bellows due to internal fluidpressure and there is also provided a fluid braking system suitable foruse. with the new brake in beaming operations. The new system evenly andadequately compensates for the change in diameter of the yarn supply onthe section beams and results in the warp being maintained under asubstantially constant tension at all times.

It is .a feature of the new brakes of this invention that they displaysubstantially no hysteresis effect and the amount of braking torqueexerted by the brake with a given fluid pressure in the bellows issubstantially the same irrespective of whether the selected pressure isapproached from a lower value or from a higher value. This advantage ismade possible only by a brake design which eliminates any part,necessary for the actual activation of the brake, moving frictionallyagainst another except,of course, the braking surfaces." In fact,substantially the only operating friction in the new brakes of thisinvention is that resulting from the flow of the braking fluid and asthis friction is completely dynamic in nature, the brakes are responsiveto practically infinitesimal changes 'in the pressure of the activatingfluid.

It is a further feature of the new brakes of this invention that theyexhibit a near perfect linear response or in other words the brakingtorque is directly proportional to the pressure in the fluid system. Infact, not only does each individual brake display an almost perfectlinear response, but each of a number of brakes of the same designgenerally gives substantially the same braking torque with a given fluidpressure even though the brakes have been subjected to different amountsof wear. As can be seen, this more readily permits the new brakes to beemployed in a system using automatic control where it is desired thatthe same braking torque be applied to a plurality of rotating members.

Further features of the new brakes of this invention are that the brakespossess an absolute minimum of moving parts, are simple in design andhave a large braking area compared to the size of the brake. Thesefeatures result -braking torque on all of the section beams issubstantially the same thereby insuring that the beams will run out atsubstantially the same'time with the elimination of soft waste.

It is a further advantage of the new braking system when applied tobeaming apparatus that the tension in the warp is maintainedsubstantially constant at all times irrespective of the diameter of theyarn supply on the section beams thereby insuring that the warp will bewound on the warp beam at a constant tension.

Still another feature of the new braking system is that it providesmeans responsive to the diameter of the yarn supply and means responsiveto the tension in the Patented Feb. 16,1960

v 3 I warp which are adapted to be employed in combination orindividually to control the braking torque applied to the section beams.

, A preferred embodiment of the invention will now be described withreference to the accompanying drawings in which:

Figure l is a fragmentary perspective view, showing principal parts inlocation, of a sizing apparatus employing the new brakes and brakingsystem.

Figure 2 is a schematic diagram illustrating the new braking system.

Figure 3 is a view in perspective of the new brake as applied to asection beam.

.Figure 4 is a sectional view of the new brake taken substantially alongthe line 4, 4 in Figure 5.

Figure 5 is a sectional view of the new brake looking substantiallyalong the line 5, 5' in Figure '4.

Referring to the drawings in greater detail, there is illustrated inFigure 1 a conventional rayon slashing apparatus modified to employ thenew brakes and braking system of this invention. Certain elements of therayon slashing apparatus such as the creel and warp beam are notillustrated as they are conventional indesign and form no part of thepresent invention.

A pluralityof section beams each of which has been previously wound witha multitude of yarn ends, are arranged in two tiers and feed yarn endsto a comb- 11. After passing through the comb 11, yarn ends from all ofthe section beams 10 are combined into a warp 12 which is drawn over aroller 13 and into a size box 14' where it is coated with a suitablesizing solution. The warp 12 is subsequently passed over drying rollers15 and is eventually collected on a warp beam, not illustrated. 7

Each of the section beams 10 has a barrel section 16 on which the warpends are wound and a head or flange 17 at each end of the barrelportion. Extending centrally from each of the heads 17. is a journal orgudgeon 18 on which the section beams are adapted to be journaled forrotation. Mounted around the gudgeon 18 on one end of each of thesection beams 10 is a fluid activatable brake, generally indicated bythe reference numeral 19, to be more specifically described insubsequent paragraphs. I p

Each of the brakes 19 is operatively connected to a header 20 which, asbest shown in Figure 2, is connected to a pump 21 through a conduit 22containing a check valve 23, a filter 24 to remove any suspended matterfrom the fluid, a valve 25, a controllable pressure regulator 26, aconstriction such as needle valve 27, anda two-way selector valve 28. Anair reservoir 29 is operatively connected to conduit 22 between thecheck valve 23 and the filter 24 and serves thepurpose of smoothing outfiuctuations in pressure introduced bythe operation of the pump 21 andalso serves, in combination with the check valve 23, as a fail safemechanism so that in the .event preceding the connection 31 by means ofa conduit 33 and a valve 34. A safety valve 35 is'connected into conduit22 at a point intermediate the selector valve 28 and the header 20 as aprecautionary measure to prevent the pressure being applied to thebrakes from rising above a safe value.

A by-pass 36 containing a pressure regulator 37 is connected to conduit2.2 eta ppipt intermediate the filter '24 and valve 25 and to thetwo-way selector valve 28.

A pressure indicator 38 is provided for measuring the pressure of fluidin by-pass 36 between the pressure regulator 37 and the two-way selectorvalve 28. A second by-pass 39 containing valve 40 is operativelyconnected at one end to conduit 22 at a point intermediate the filter 24and valve 25 and at the other end to a connection 41 immediatelyfollowing the valve 27.

The pressure regmlating means 26 is operated by a feeler arm 42 pivotedatone end from a suitable support 43 and having at the other end acontact for the yarn supply on beam 10 such as a small rollerindicatedfby the reference numeral 44. The roller 44 is preferably madeof a light weight material such as cork and is adapted to be heldagainst the surface of the yarn supply on a selected one of the beams 10by the tension spring in the regulator 26. As the diameter of the yarnsupply on the section beam 10 decreases, a corresponding movement of theroller 44 and arm 42 allows pressure regulator 26 to close and decreasethe pressure being supplied to brakes 19 by conduit 22.

After the warp 12 passes through comb 11 it is passed over a stationaryrod 45 and then under a rod 46 which is resiliently mounted by virtue ofleaf springs 47 only one of which is shown. The warp is then passedupwardly over roller 13 so that the rod member 46 is displaced upwardlyas a result of the tension in the warp and as will be apparent to thoseskilled in the'art, the degree of displacement of the rod 46 will bedependent on the tension in the warp 12. The nozzle 32 is'positionedimmediately below the spring member 47 so that the spring member acts asa variable closure for the nozzle.

In operation, the slashing apparatus is p'rovided'with full sectionbeams, pump 21 is started to build up suitable operating pressure, andthe selector valve 28 is positioned to open by-pass 36. Pressureregulator 37 is opened sufiiciently to give approximately the correctbrakingpressure and the slasher is placed in operation, Pressureregulator 37 is then adjusted to give exactly the desired brakingactionas determined visually. The reading of pressure indicator.38 isnoted and with the selectoryalve 28 still in the position to openby-pass 36, and with needle valve 27 wide open and valve 34 closed,pressureregulator 26 is adjusted to give a reading on pressure'indicator 30 slightly in excess of that on pressure indicator 38. Valve34 is. then opened and no'zzle32 positioned with respect to the springmember '47 so that' the escape of fluid from nozzle 32 is appreciablebut not excessive. As pressure regulator 26 will be trying dili- 'offiuid from nozzle 32'.is thenagain'checked to make certain it issatisfactory in volume and'if necessary readjustment of nozzle-32 andneedle valve 27 is made.

vWhen the escape of fluid from nozzle 32 is satisfactory and the readingof pressure indicator 30 is identic'al to that of pressure indicator 38,selector valve 28 is operated to close by-pass 36 and open conduit 22.

As has been previously explained, it is necessary that the brakingaction be decreased as the. diameter of the yarn supplyon the sectionbeams decreases in order that the tension in the warp be maintainedconstant. It will be apparent from the above description that'this isaccomplished by pressure regulator 26 providing a decreased pressure on;the fluid 'being supplied to brakes 19 by reason of 'the movement of arm42 with decreasing yarn supply diameter. Pressure regulator 26 is,therefore, the primary pressure regulating means and the purpose of .theescape nozzle 32 in ordinary operation is that of a econdary pressureregulating means re ponsive to, arp

' warp -12 increase above the desired value,

6 sure indicator close .by pass 36 p I the brakes. through by-pass39,conduit 22 and header slightly, the-rod-46sis l oyveredlasa resultof thetension ing spring rrten bersz 47, thereby decrea fn'g the volume of fllidescaping'throughlthe nozzle 32 so that the'fluid pres- .sure beingsupplied to brakes 19 isequal to-the pressure in conduit 22;:betweenpressure regulator 26 and needle valve 27.; ;On;the other hand shouldthe tension in red 46 "and spring; niembers 47 ateraised yer'ticallythereby, allowing I an increasedescape of fluidlfromnoz'zle 32. Due tothe constriction: in conduit -2j2 furnished by valve 27, this resuli ina reduced fluid pre ssure being applied to the fluid st vatab e b kes.lhsothat the nsion,. in th p i I 1' T. i i .l .-It is a feature of thepresent braking system that it be operated with either .nozzle132. or.pressure regu- .lator26.servi ng .as the sole pressure regulating.meansfand this is advantageous in rrumerous instances; I f for 'examplepump 21 becomes defectiveso that it is incapable of furnishingsuflicient'fluid to operate the system when escape nozzle. 32 is li;noperation, it' may be desirable to operate thebrakingnsystem solely'byimeans of pressure regulator 26.. on thelotherhandgit the'ipressureregulator 26qshould becomedeiectiye in I acition, one mightdesire tooperate.the systernfwith escape nozzle 32 as the sole pressureregulating means.

To operate the braking system with regulator 26 as .the soleregulatingrneansa correct operating pressure is de e min as exp aincda ey.- b -P ss, 6am P es- ;sure indicator 38. With valve 34 elosed andvalve 27 regulator 2,6.is' then adjusted so thatpr'es- 3.0; gives a'reading identical to that of Theselector valve 28" is then operated toope p s e close. by.-pas s .36 {and open conduit 22. i

braking system with escape nozzle 32 To operate the as thesole'pr'essure regulating means, acorrect operating pressureisdeterminedby. means of. by-pass 36.as .above an ith, v lva ficl e -{and a es M ndp n nozzle 32 is positipnedtogivea' pressure reading on indicatorequaljto that on indicator 38. If the escape of fluid from nozzle isexcessive; valve 40 should be partially clo'sedyand' nozzle 32 again.adjusted to give a correct pressure reading on indicator 30. When theescape of fluid'fron'i nozzle 32 issatisfactory and the reading ofpressure 'indicator"30'.i s identica tdthat of essure indicator 38,selectorvalve 28 is operated to so that fluid pressure is then suppliedto i t t l Reference will now'be titadeto Figures 3, 4=and5 of ."thedrawings"wherem the new fluid activatable brake is illustrated ingreater detail. T he'reference'nurneralSt) designates a tubular sleeveadaptedto be placed over a gudgeon 18 extending centrally from the head17 of a section beam. As gudgeons of various section beams vary slightlyin diameter, an adapter sleeve 51 is provided to eliminateneedless play.Sleeve is provided with an annular flange 52 near one end and attachedto the flange 52 by any suitable means such as by bolts 53 is acentrally apertured, disk shaped member 54 having a wide peripheralannular flange 55. Secured to the flange member 55 for instance bywelding is a lug member 56 adapted to engage any one of a number of ribs57, with which the heads of section beams are conventionally provided,and thereby secure the'disk member 54 and sleeve 50 for rotation withsection beam 10.

J ournaled'about sleeve 50 and free to rotate with respect thereto byvirtue of low frictionrbearings 58 and 59 is a cylindrical housing 60.The housing 60 is secured against lateral movement by a grease retainerring 62 rib 57 0f the section beam head 17, the section beam is:effectively braked. As will be apparent, the magnitude of the brakingtorqueis dependent on the internal prestional creel standard 86.

member 54.

rotate because of its attachment to bellows 67'and housgames and locl;nuts 63: and 64 threaded onto sleeve- 50. The housing 60 is providedwith a pair 0t opposed arcuate flanges65 to which an end member 66 of atoroid shaped bellows 67 is. attached-by any Suitable means suchas by'bolts 68. The opposite end'member 69 of the toroid shaped bellows 67serves as a brake shoe to which'there is attached a section of brakelining material-70 by any suitable means such as by screws 71 havingtheir heads recessed within the brake lining material. 'The brakingsurface of brake shoe member 69 is adapted to frictiona'lly engage theinner surface ofthe diskmember 54 which, of course, is machined to ahigh degree of smoothness to present a suitable braking surface and toeliminate unnecessary abrasion of the brake lining 70. The brakingsurfaces as well as the flexible part of bellows 67 are protected fromexternal dirt and lint by means 55 whichserves as a protective cover.Mounted through the brake shoe 69 in spacedrelationship to the housing60 is an inertia ring member 72 having anfannular flan'ge73. The innerperipheral edge of brake lining 70 is provided-with a-nannular recess 74to'receiveth flange 73 which; is maintained-in sliding frictionalcontact with the brake lining 70 by means of a number of clip springs 75The springs 75 are mounted in suitable recesses 76 in the brake liningmaterial and aresecured to the brake drum member 69 by screws 77. Theend member 66 of the bellows 67 is provided with an orifice 78 intowhich. a suitable-fitting 79 is threaded. The fitting 79 is' connectedby a suitable conduit 80 to header 20 '(Figure 1) for the supply of afluid under pressure.

The housing 60 1s provided with a-pair of trunnions '81 suitable forsupporting the same in a trunnion box 82 quite similar to that withwhich creels are conventionally equipped. The trunion box 82 ispivotally secured to a slide, not illustrated, but conventional inconstruction,

which in turn is mounted in a housing 83 and is movable laterally in aconventional manner by rotation of the wheel 84. The housing '83 is inturn rigidly attached by any suitable means such as a bolt 85 to aconven- In operation, the bellows 67 is expanded lengthwise by internalpressure above atmospheric by means of a fluid being admitted throughconduit 80 andfitting 79. Onexpansionof the bellows 67, the brake liningmaterial 70f'rictionally engages the smooth surface of rotating disk.Sincethebrake lining 70 is not free to ing 60, a braking torque isexerted on disk member 54 and since disk member 54 is secured forrotation with the section beam 10 by means of lug 56 bearing againstsure in bellows 67 which can be etfectively varied by changing thepressure on the fluid being supplied through conduit 80. w f

-The brake lining 70- is secured against rotation only. by

virtue of its attachment to the free end of bellows 67 and since bellows67 is not completely torsionally rigid, this'introduces the likelihoodof high frequency vibration of the brake shoe member 69. The inertiaring member 72 provides means for effectively damping the high frequencyvibration which may possibly result because of this arrangement. Whilethe inertia ring 72 does not prevent rotation of the brake shoe member69, it momentarily discourages transient actions because of the inertiaof the ring and the sliding frictional contact of the flange 73 with thebrake lining 70 so that the brake shoe member 69 is eflectivelyprevented from oscillating in a rotary manner.

Having thus described out invention, what we desire to claim and protectby Letters Patent is:

We claim:

1. A fluid activated brake for applying braking torque tachment to saidbellows and thetorsional rigidityof said bellows, and damping meanscomprisingan inertia' ring mounted in slidingfrictional contact withsaid brake shoe.

2. In a beaming apparatus, a brake comprising a sleeve adapted toencircle the gudgeon of a beam, a disk shaped brake member carried bysaid sleeve, means adapted to secure said disk member for rotation-withthe beam, a

cylindrical housing journaled about said sleeve, a toroid shaped bellowscircumscribing said housing, said bellows being secured at one end'tosaid housing, a disk shaped brakeshoe carried by the free end of saidbellows for engaging said disk member on expansion of said bellows,saiddisc-shaped brake shoe being restrained from rotation only byattachment to said bellows and the torsional rigidity of said bellows,an inertia ring carried by the free vend of said bellows to damp highfrequency vibration of said brake shoe, and means on said cylindricalhousing for supporting the housing in a creel'and securing the sameagainst rotation. I

3. ha beaming apparatus, a'braking system compris ,ing a sleeve adaptedto incase the gudgeon of abeam,

a, disk shaped brake member carried by said sleeve, a lug member on saidbrake member adapted to engage a rib on a beam head whereby said brakemember is secured for rotation with the beam, a cylindrical housing.journaled about said sleeve, a toroid shaped bellows positioned aboutsaid housing and secured at oneend to said housing, a centrallyapertured, disk shaped brake shoe positioned in spaced relationshipabout said housing and carried by the free end of said bellows,- saidbrake shoe having a lined surface for frictionally engaging said diskshaped brake member on expansion of said bellowsfa flanged annular.inertia member positioned through said centrally ap'ertured brake shoein spaced relationshipto lows as the diameter of the yarn supply on saidbeam decreases.

brake shoe being restrained against rotation only by at- 1 said housing,a recess in the brake lining to receive the flange ofysaid annularinertia member, a plurality of resilient retaining members secured tosaid brake shoe to retain the flange of said inertia member in slidingfrictlonal contact with said brake lining, a pair of trunnions on saidcylindrical housing for supporting said housing in a creel and to securethe same against rotation, and a fluid supply system to-supp'ly a fluidunder pressure internally 'to said bellows. 1

4. A braking system as in claim 3 whereinsaid fluid supply system isprovided with means for automatically decreasing the pressure of thefluid supplied to said bel- SJj'A fluid activated' jbr ake for applyingbraking torque to'a rotatable rne'mber'fsaid brakecomprisingin'combination a substantiallyflabfaced'braking surface adapted forrotation aboutthe axis of rotation of said rotatable 'memberin fixed"relationship therewithfa torsionally rigid bellows'expandable lengthwiseby internal pressure, said bellows being secured at one end to preventrotation with said rotatable rrien'tber,- a secondsubstantiallyflat-faced braking surface operatively conrlected-to-and supported.by'said bellows and designed *tofrictio'nally engage said first surfaceupon'expansion of said bellows and tobe f'r'eelyldisengageable from saidfirst surface upon contraction of said bellows; said second brakingsurface being restrained from rotatiodonly by the torsional rigidity ofsaid bellows; and an inertial dampinge lement operatively connectedinenergy absorbing relationto and movable relative to said second brakingsurface to inertially absorb energy from and thereby dampvibrationof'said second braking surface. 1 I 1 '6, YA brake arrangementaccordin'gto claim 5 wherein said bellows :isjin the shape of 'a,toroidcircu'mscribing the axis of rotation of said rotatable member.

7. A fluid activated brake fonapplying'braking torque to a rotatablemember; saidbrakekomprising a first disk shaped"brakin'gsurfacerotatableabout the axis of rota- ,tion of said rotatable member in'fixedrelationship therewith, a torsiorially rigid bellows expandablelengthwise by internal fluid pressurefsaid bellows being secured at oneend to prevent'rotation' with said rotat'able member, a second diskshaped braking surface attached to the free end of said'bellows forfrictionally engaging said first braking surfaceupon expansion of saidbellows, said second braking surface being' restrain'ed from rotationonly byjattachment tos'aid bellows,'and the torsional rigidity of saidbellows, and an inertial damping element operatively'conne'ctedin'energy absorbing "relation to'and movable relative to said second diskshaped braking surface to inertially absorb-energ from and thereby'damphigh frequency vibration of said second disk shaped braking v n t t v l.l a t. f I '8. Abra'ke arrangementaccording to 'claim 7 wherein Y saidbellows 'is' in the shape'ofa toroid'circumscribingthe axis ofrotation'ot' said 'rotatable'member.

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